JP2015152148A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent fretting friction based on elastic deformation of an input-side disk 2c in an axial direction caused by thrust of a pressurization device.SOLUTION: A spline shaft part 13a is arranged at a portion closer to an outer peripheral face of a tip part of an input rotating shaft 1b, and a lock recessed groove 14a and an outer peripheral side cylindrical face part 22 having an outside diameter larger than a diameter of a circumscribed circle of the spline shaft part 13a are arranged in a state that the spline shaft part 13a is sandwiched between both sides in an axial direction. The spline shaft part 13a and a spline hole 12a which is formed at an intermediate part of a center hole 18 of an input-side disk 2c in the axial direction are engaged with each other, and the outer peripheral side cylindrical face part 22 and an inner peripheral face side cylindrical face part 20 formed at an inner end part of the center hole 18 are fit and fixed to each other by interference fitting. Then, an outside face of an inner-oriented flange part 21 formed at an outer end part of the center hole 18 and an inside face of a lock ring 15a are made to abut on each other.

Description

  The present invention relates to an improvement in a toroidal type continuously variable transmission that is used as a transmission for an automobile or a transmission for adjusting the operating speed of various industrial machines such as a pump.

  The use of a toroidal continuously variable transmission as a transmission for an automobile is described in many publications such as Patent Documents 1 to 4 and partially implemented, and is well known. Further, a structure in which a toroidal type continuously variable transmission and a planetary gear mechanism are combined to widen the adjustment range of the gear ratio is also described in many publications such as Patent Document 5 and has been widely known. FIG. 2 shows a first example of a toroidal-type continuously variable transmission described in these patent documents and widely known in the past. In the case of the first example of this conventional structure, a pair of input-side disks 2a and 2b are disposed around the portions near both ends of the input rotation shaft 1, and axial one side surfaces, each of which is a toroidal curved surface having a circular arc cross section, are mutually connected. In a state of being opposed to each other, it is supported via ball splines 23 and 23 so as to be movable in a near-far direction and to rotate in synchronization with each other via the input rotary shaft 1. An output cylinder 3 is supported around the intermediate portion of the input rotary shaft 1 so as to be able to rotate relative to the input rotary shaft 1. Further, on the outer peripheral surface of the output cylinder 3, an output gear 4 is fixed at the center in the axial direction, and a pair of output side disks 5, 5 are connected to both ends in the axial direction by spline engagement. The rotation synchronized with 3 is supported. Further, in this state, the axial side surfaces of the output side disks 5 and 5, each of which is a toroidal curved surface having an arcuate cross section, are opposed to one axial side surface of the input side disks 2 a and 2 b. .

  Further, a plurality of power rollers 6 and 6 each having a partially spherical convex surface are sandwiched between the input disks 2a and 2b and the output disks 5 and 5. The power rollers 6 and 6 are rotatably supported by the trunnions 7 and 7 and rotate with the rotation of both the input side disks 2a and 2b. Power is transmitted to the output side disks 5 and 5. That is, during operation of the toroidal-type continuously variable transmission, the drive shaft 8 pushes one (left side in FIG. 3) the input side disk 2a and the pressing device 9 (the structure shown in the drawing is a mechanical pressing device having a loading cam type). However, a structure using a hydraulic type in which a piston is fitted in a hydraulic cylinder is also widely known in the art. As a result, the pair of input-side disks 2a and 2b supported at both ends of the input rotation shaft 1 rotate synchronously while being pressed in a direction approaching each other. Then, this rotation is transmitted to the output side disks 5 and 5 through the power rollers 6 and 6 and is taken out from the output gear 4. The trunnions 7 and 7 correspond to the support members described in the claims. On the other hand, in the case of a full toroidal toroidal continuously variable transmission, the carrier corresponds to the support member described in the claims.

  Further, preload springs 10a and 10b are provided at positions where both the input side disks 2a and 2b are sandwiched from both sides in the axial direction in the vicinity of both ends of the input rotary shaft 1, respectively. Even when the pressing device 9 is not in operation (when the drive shaft 8 is stopped), the peripheral surfaces of the power rollers 6 and 6 and the inner surfaces of the input side and output side disks 2a, 2b and 5 are provided. The surface pressure of the rolling contact part (traction part) is secured to the minimum necessary. Therefore, these rolling contact portions start power transmission without causing excessive slip immediately after the start of operation of the toroidal continuously variable transmission. The elasticity for securing the minimum necessary surface pressure is obtained by a preload spring 10 a disposed on the inner diameter side of the pressing device 9. The preload spring 10b disposed between the loading nut 11 screwed to the tip end of the input rotary shaft 1 and the outer surface of the input side disk 2b alleviates the impact applied when the pressing device 9 is suddenly operated. It can be omitted. When it is provided, it has a sufficiently large elasticity (so as not to be completely crushed even when a large torque is transmitted).

  In the case of the toroidal type continuously variable transmission as described above, the work of adjusting the elasticity of the preload spring 10a for ensuring the minimum surface pressure is troublesome. That is, in the case of the first example of the conventional structure, it is necessary to adjust the elasticity of the preload spring 10a by changing the tightening amount of the loading nut 11 screwed to the tip end portion of the input rotary shaft 1. It is. On the other hand, Patent Documents 6 to 7 describe a structure using a locking ring called a cotter instead of a loading nut.

  3 to 6 show a second example of a conventional structure in which such a locking ring is incorporated. In the case of the second example of this conventional structure, a spline hole 12 is formed at the center of the input side disk 2b, and the spline hole 12 and a spline shaft portion 13 formed on the outer peripheral surface of the input rotary shaft 1a. Is engaged. Further, a locking groove 14 is formed on the outer peripheral surface of the tip end portion of the input rotating shaft 1a in the axial direction away from the spline shaft portion 13 over the entire circumference. The radially inner half of the locking ring 15 composed of a plurality (2 to 4) partial arc-shaped elements is locked. Then, the radially outer end portion of the inner side surface (left side surface in FIGS. 3 to 4) of the locking ring 15 is brought into contact with the radially inner end portion of the outer side surface of the input side disk 2b. When the pressing device 9 (the structure shown in FIG. 3 is a hydraulic pressing device) is not operated, the peripheral surfaces of the power rollers 6 and 6 (see FIG. 2) and the input and output side disks 2a, 2b and 5a For the adjustment of the elasticity of the disc spring 10a in order to ensure the necessary minimum surface pressure of the rolling contact portion with the inner side surface, the one having the appropriate axial thickness dimension is selected as the locking ring 15 Plan by things. Further, a retaining ring 16 having an L-shaped cross section is fitted on the tip of the input rotating shaft 1a, and the inner peripheral surface of the retaining ring 16 is brought into contact with or in close proximity to the outer peripheral surface of the locking ring 15. This locking ring 15 (each element constituting the locking ring 15) is prevented from coming out of the locking groove 14. Such a retaining ring 16 prevents axial displacement by a retaining ring 17 that is engaged with the tip of the input rotary shaft 1a. With the configuration described above, the input disk 2b is supported on the input rotary shaft 1a so as to be able to rotate in synchronization with the input rotary shaft 1a. In the case of the second example of the conventional structure, the entire toroidal continuously variable transmission is reduced in size and weight by using an integral output side disk 5a. However, since the structure and operation of this part are not related to the gist of the present invention and are widely known in the past, detailed description will be omitted.

  In the case of the toroidal type continuously variable transmission according to the second example of the conventional structure as described above, the input-side disk 2b on the distal end side is driven by the power rollers 6 based on the thrust generated by the pressing device 9 during operation. Based on the force received from 6, as shown exaggeratedly in FIG. 7, the portion closer to the outer diameter of the input side disk 2 b is elastically deformed in the direction approaching the locking ring 15 side (axial direction). That is, the force applied to the input side disk 2b based on the thrust during operation is about several tens kN to hundreds tens kN (several tF to several tens tF) at the maximum during operation of the toroidal type continuously variable transmission. The amount of elastic deformation in the axial direction of the input-side disk 2b based on a large force is a comma number of mm (a few tenths of a millimeter) and cannot be ignored. When the input side disk 2b is elastically deformed in the axial direction in this way, there is a possibility that the outer side surface of the input side disk 2b and the inner side surface of the locking ring 15 are repeatedly contacted intermittently. In the case of the second example of the conventional structure, since the spline hole 12 is provided at the center of the input side disk 2b, the outer edge of each female spline groove of the spline hole 12 (the right end in FIGS. 3 and 4). Edge) and the inner side surface (the left side surface in FIGS. 3 and 4) of the locking ring 15 repeatedly abut against each other and rub against each other, and the outer end edges of each of these female spline grooves (of each of these female spline grooves) The outer end radial direction inner edge of the spline crest existing on both sides in the circumferential direction tends to bite into the inner surface of the locking ring 15, and fretting wear may occur in that portion.

  In particular, the circumferential position at which the input side disk 2b is elastically deformed always changes as the portions pressed by the power rollers 6 and 6 change. For this reason, the frequency of the rubbing is considerably high (for example, hundreds of tens Hz) due to the fact that the number of the spline crests is large, which is a severe condition in terms of occurrence of fretting wear. Such fretting wear may become a starting point of damage such as peeling, or the generated wear powder may contaminate the lubricating oil (traction oil), resulting in poor lubrication of each part. In particular, the fretting wear on the inner surface of the locking ring 15 based on repeated contact between the outer edge of each female spline groove of the spline hole 12 and the inner surface of the locking ring 15 is caused by the diameter of the inner surface. A step portion is formed in the middle portion in the direction. Such a stepped portion has a large (as high as several tens of kN to hundreds of tens of kN) as described above from the input side disk 2b to the outer diameter portion of the locking ring 15 during operation of the toroidal type continuously variable transmission. ) When a thrust load is applied, a large bending stress is likely to occur partially, which may cause a serious damage such as a crack that leads to a loss of the supporting force of the locking ring 15.

JP 2003-214516 A JP 2007-315595 A JP 2008-25821 A JP 2008-275088 A JP 2004-169719 A JP 2000-205361 A JP 2009-041715 A

  In view of the circumstances as described above, the present invention provides an edge of a female spline groove of a spline hole provided at the center of the outer disk, and an engagement ring, regardless of the elastic deformation in the axial direction of the outer disk. The invention was invented to realize a structure capable of preventing fretting wear from occurring on one side surface.

The toroidal-type continuously variable transmission of the present invention is similar to the previously known toroidal-type continuously variable transmission, and includes a rotating shaft, a pair of outer disks, an inner disk, and a plurality of support members. The same number of power rollers as the support members, a pressing device, and a locking ring are provided.
Among these, the rotating shaft is provided with a locking groove extending in the circumferential direction on the outer peripheral surface of the tip portion, and a spline shaft portion is provided in a portion adjacent to the locking groove in the axial direction.
In addition, the both outer disks can freely rotate in synchronization with the rotating shaft at both ends of the rotating shaft in a state where the axial side surfaces of each of the toroidal curved surfaces each having a circular arc cross section are opposed to each other. One outer disk of the two outer disks is capable of axial relative displacement with respect to the rotation axis, and the other outer disk is a spline hole formed at the center of the other outer disk. Each is supported by engaging the spline shaft portion.
In addition, the inner disk has a circular arc-shaped toroidal curved surface around the middle part of the rotating shaft, with the axially opposite side surfaces facing the axially one side surface of the outer disk, and with respect to the rotating shaft. The relative rotation is supported freely, and it is formed as a single unit or a pair of elements.
Further, each of the supporting members is pivoted at a position twisted with respect to the rotating shaft, and a plurality of each of the supporting members is disposed between the axial side surfaces of the inner disk and the axial side surfaces of the outer disks. Oscillating displacement about the center is provided.
Each of the power rollers is rotatably supported by each of the support members, and each circumferential surface having a partially spherical convex surface is formed on both axial sides of the inner disk and axial pieces of the outer disks. It is in contact with the side.
The pressing device is provided between the rotating shaft and one outer disk of the two outer disks, and the one outer disk faces the other outer disk of the two outer disks. Press. As such a pressing device, a mechanical pressing device incorporating a loading cam or a hydraulic pressing device including a hydraulic cylinder and a piston can be used.
In addition, the locking ring is configured by combining a plurality of (for example, 2 to 4) partial arc-shaped elements so as to form a ring shape as a whole, and the locking ring formed on the outer peripheral surface of the rotating shaft. Locked in the groove, one axial side surface of the locking ring (a portion exposed from the locking groove) is brought into contact with the other axial side surface of the other outer disk facing in the axial direction. . This prevents the other outer disk from being displaced in a direction away from the one outer disk.

  Particularly, in the case of the toroidal type continuously variable transmission according to the present invention, the axial side surface of the locking ring and the edge of each spline groove constituting the spline hole are separated from each other in the axial direction, and the power rollers Even when the other outer disk is elastically deformed due to torque transmission between the disks via the rim, one axial side surface of the locking ring and the edge of each female spline groove constituting the spline hole Is prevented from coming into contact.

Preferably, when the present invention as described above is carried out, as in the invention described in claim 2, the spline shaft portion is sandwiched from both sides in the axial direction on the outer peripheral surface of the distal end portion of the rotating shaft, and the locking is performed. The outer circumferential surface side cylindrical surface portion having an outer diameter larger than the diameter of the circumscribed circle of the concave groove and the spline shaft portion and extending in the axial direction is provided. In addition, an inner peripheral surface side cylindrical surface portion whose outer diameter does not change in the axial direction is provided at an end portion on the other axial side surface adjacent to the spline hole in the inner peripheral surface of the other outer disk. And this inner peripheral surface side cylindrical surface and the said outer peripheral surface side cylindrical surface part are fitted by interference fitting.
Preferably, as in the invention described in claim 3, an inner diameter smaller than the diameter of the inscribed circle of the spline hole is formed at the end of the other side in the axial direction of the inner peripheral surface of the other outer disk. An inward flange portion is formed, and the inward flange portion is disposed between one axial side surface of the locking ring and an inner surface of the locking groove. Then, the other axial side surface of the inward flange is brought into contact with the one axial side surface of the locking ring.

  According to the toroidal type continuously variable transmission of the present invention configured as described above, regardless of the elastic deformation in the axial direction of the outer disk, the edge of the female spline groove of the spline hole of the outer disk, and the locking ring It is possible to prevent fretting wear from occurring between the one side surface and the other side surface. In other words, one axial side surface of the locking ring and the edge of each spline groove constituting the spline hole are separated from each other in the axial direction. As a result, even when the outer disk is elastically deformed in the axial direction based on the thrust generated by the pressing device, the one axial side surface of the locking ring and the end edge of the female spline groove are rubbed together. It is possible to prevent the edge from becoming a tendency to bite into one side surface in the axial direction, and to prevent the occurrence of significant fretting wear in the portion.

  Further, as in the invention described in claim 2, the outer peripheral surface side cylindrical surface portion provided on the rotating shaft side and the inner peripheral surface side cylindrical surface portion provided on the other outer disk side are fitted by an interference fit. In the case of the structure, the concentricity between these rotating shafts and the other outer disk side (the accuracy with which the center axes of these rotating shafts and the other outer disk side coincide with each other during assembly) can be improved. Support rigidity between the rotating shaft and the other outer disk can be improved. In other words, the support rigidity is not only improved based on the interference fit between the cylindrical surface portions, but also the rotational shaft and the other outer disk side are arranged at a plurality of positions in the axial direction (the relationship between the spline shaft portion and the spline hole). And a mating portion, a butting portion between one axial side surface of the locking ring and the other axial side surface of the other outer disk, and a fitting portion between the outer peripheral surface side and the inner peripheral surface side cylindrical surface portions). Therefore, also from this aspect, it is possible to improve various performances of the toroidal type continuously variable transmission by improving the support rigidity and improving the accuracy of gear ratio adjustment by improving the positioning accuracy of the other outer disk. Further, according to the structure of the invention described in claim 3, the axial distance (support span) of the support portions at a plurality of positions separated in the axial direction, which supports the other outer disk side with respect to the rotating shaft, is provided. The support rigidity related to the moment applied to the other outer disk can be further improved based on the thrust generated by the pressing device, and the various performances of the toroidal continuously variable transmission can be further improved.

The figure (A) equivalent to the X section enlarged view of FIG. 3 which shows an example of embodiment of this invention, and the Y section enlarged view (B) of (A). Sectional drawing which shows the 1st example of a conventional structure. Sectional drawing which shows the 2nd example. Similarly, the X part enlarged view (A) of FIG. 3, and the Z part enlarged view (B) of (A). The perspective view which takes out and shows the input side disk of the front end side. Sectional drawing which shows the state of the engaging part of this input side disk of this front end side, and an input rotating shaft. The schematic diagram which exaggerates and shows the elastic deformation of this input side disk of the front end side.

[Example of Embodiment]
FIG. 1 shows an example of an embodiment of the invention corresponding to all claims. The features of the toroidal continuously variable transmission and continuously variable transmission of the present invention, including this example, are described in the claims based on the thrust generated by the pressing device 9 (see FIGS. 2 and 3). Regardless of the elastic deformation of the input side disk 2c which is the other outer disk, the outer end edge (right end edge in FIG. 1) of the female spline groove of the spline hole 12a formed at the center of the input side disk 2c, The fretting wear is prevented from occurring between the inner side surface (left side surface in FIG. 1) that is one side surface of the ring 15a in the axial direction. Since the structure and operation of the other parts are the same as those of conventionally known toroidal type continuously variable transmissions including the structures shown in FIGS. 2 to 6 described above, illustration and explanation of equivalent parts are omitted or simplified. In the following, the characteristic part of this example will be mainly described.

  In the case of this example, the spline hole 12a is provided in the central portion of the input side disk 2c only in the middle portion in the axial direction of the center hole 18 provided in a state of passing through the input side disk 2c in the axial direction. ing. Of the both axial ends of the center hole 18, a cross section relating to an imaginary plane orthogonal to the central axis of the input side disk 2c is formed at the inner end that is the end on the support post 19 side for supporting the output side disk 5a. The inner circumferential surface side cylindrical surface portion 20 is a perfect circular shape with no distortion and the inner diameter does not change in the axial direction. On the other hand, the diameter of the inscribed circle of the spline hole 12a is formed at the outer end, which is the end opposite to the support post 19 for supporting the output-side disk 5a, of the both ends in the axial direction of the center hole 18. An inward flange 21 having a smaller inner diameter is formed.

  On the other hand, a spline shaft portion 13a that is spline-engaged with the spline hole 12a at a portion near the outer peripheral surface of the tip end portion (the right end portion in FIG. 1) of the input rotation shaft 1b that is the rotation shaft described in the claims. In the state where the spline shaft 13a is sandwiched from both sides in the axial direction, a locking groove 14a for locking the inner half of the locking ring 15a and a diameter of a circumscribed circle of the spline shaft 13a An outer peripheral surface side cylindrical surface portion 22 having a larger outer diameter is provided. The outer peripheral surface side cylindrical surface portion 22 has a cross-sectional shape with respect to a virtual plane orthogonal to the central axis of the input rotation shaft 1b, which is a regular circle without distortion, and the outer diameter does not change in the axial direction. Further, the outer diameter of the outer peripheral surface side cylindrical surface portion 22 in a free state is slightly larger than the inner diameter of the inner peripheral surface side cylindrical surface portion 20 in a free state. Then, in a state where the toroidal-type continuously variable transmission is assembled, the spline hole 12a and the spline shaft portion 13a are spline-engaged, and the inner peripheral surface side cylindrical surface 20 and the outer peripheral surface side cylindrical surface portion 22 are connected. It is fitted with an interference fit.

Further, the axial width W _14a of the locking groove 14a is sufficiently larger than the axial width W ₁₄ (see FIG. 4) of the locking groove 14 of the conventional structure shown in FIG. slightly larger than the sum of the axial thickness _{T 15} of the retaining ring 15a and an axial thickness _{T 21} of the inward flange portion 21 is _{{(W 14a> (T 15} + T 21)> W 14}. And in the state which assembled the toroidal type continuously variable transmission, the said inward eaves part 21 is arrange | positioned between the inner side surface of the said locking ring 15a, and the inner side surface of the said locking groove 14a, and the said inward eaves part 21 is brought into contact with the inner surface of the locking ring 15a When the toroidal continuously variable transmission is operated in this state, the pressing device 9 (see FIG. ~ 3)), the force of about several tens of kN to several hundreds of kN is applied as described above. In addition, traction oil is present at the abutting portions between the two side surfaces, and this traction oil acts as a resistance against the movement of these two side surfaces in the radial direction. In addition to the engagement portion between the spline hole 12a and the spline shaft 13a, the input rotation shaft 1b is supported by the fitting portion between the cylindrical surface portions 20 and 22 and the butting portion between the both side surfaces. Yes.

  According to the toroidal type continuously variable transmission of this example configured as described above, the axially intermediate portion of the center hole 18 of the input side disk 2c is not affected by the elastic deformation of the input side disk 2c in the axial direction. It is possible to prevent fretting wear from occurring between the edge of the female spline groove of the provided spline hole portion 12a and the inner surface of the locking ring 15a. That is, in the case of this example, the inward flange portion 21 is provided at the outer end portion of the center hole 18 of the input side disk 2c, and the inner side surface of the locking ring 15a and the female spline constituting the spline hole portion 12a. The end edges of the grooves are separated from each other in the axial direction (the inner surface of the locking ring 15a is in contact with the outer surface of the inward flange 21 whose inner peripheral surface is a simple cylindrical surface). Thus, even when the input side disk 2c is elastically deformed in the axial direction based on the thrust generated by the pressing device, the inner surface of the locking ring 15a and the edge of the female spline groove rub against each other. It is possible to prevent the edge from becoming a tendency to bite into one side surface in the axial direction, and to prevent the occurrence of significant fretting wear in the portion.

  In particular, in the case of the structure of this example, the outer peripheral surface side cylindrical surface portion 22 provided on the input rotating shaft 1b side and the inner peripheral surface side cylindrical surface portion 20 provided on the input side disk 2c side are fitted by an interference fit. As a result, the concentricity between the input rotary shaft 1b and the input side disk 2c can be improved (the amount of eccentricity and the tilt angle between the central axes can be reduced). The improvement of the concentricity leads to the reduction of vibration and the improvement of the accuracy of the gear ratio control by reducing the swinging motion of the input side disk 2c during the operation of the toroidal type continuously variable transmission.

  Furthermore, the support rigidity between the input rotating shaft 1b and the input side disk 2c can be improved. First of all, the support rigidity can be improved based on the interference fit between the cylindrical surface portions 20 and 22. In addition, the input rotary shaft 1b and the input-side disk 2c side are connected to the engagement portion between the spline hole 12a and the spline shaft portion 13a, the fitting portion between the cylindrical surface portions 20 and 22, and the inward-facing rod. The abutting portions between the axial side surfaces of the portion 21 and the locking ring 15a are supported at three positions spaced in the axial direction. Particularly in the case of this example, the axial distance (support span L) between the fitting portion and the abutting portion located at both ends in the axial direction among these support portions can be made sufficiently long. Based on the thrust generated (see FIGS. 2 to 3), the support rigidity related to the moment applied to the input disk 2c is further improved, and the central axis of the input disk 2c and the central axis of the input rotary shaft 1b are inclined. It is possible to further improve the various performances of the toroidal-type continuously variable transmission by effectively suppressing this.

  The present invention is not limited to the half toroidal type as shown in the figure, and can be implemented by a full toroidal type toroidal continuously variable transmission. Furthermore, the present invention is not limited to a continuously variable transmission combined with a differential mechanism such as a planetary gear device, and can be implemented as a single toroidal continuously variable transmission.

DESCRIPTION OF SYMBOLS 1, 1a Input rotary shaft 2a, 2b, 2c Input side disk 3 Output cylinder 4 Output gear 5, 5a Output side disk 6 Power roller 7 Trunnion 8 Drive shaft 9 Pressing device 10a, 10b Preload spring 11 Loading nut 12, 12a Spline hole 13, 13a Spline shaft portion 14, 14a Locking groove 15, 15a Locking ring 16 Retaining ring 17 Retaining ring 18 Center hole 19 Support post 20 Inner peripheral surface side cylindrical surface portion 21 Inward flange portion 22 Outer peripheral surface side cylindrical surface portion 23 Ball spline

Claims (3)

A rotation shaft, a pair of outer disks, an inner disk, a plurality of support members, the same number of power rollers as each of the support members, a pressing device, and a locking ring;
Among these, the rotating shaft is provided with a locking groove extending in the circumferential direction on the outer peripheral surface of the tip portion, and a spline shaft portion provided in a portion adjacent to the locking groove in the axial direction,
The both outer disks are free to rotate in synchronization with the rotating shaft in a state where the axial side surfaces of the toroidal curved surfaces each having an arc cross section are opposed to each other. One of the outer disks is capable of axial displacement relative to the rotation axis, and the other outer disk engages a spline hole formed at the center of the other outer disk with the spline shaft. So, it is supported by each of these rotating shafts,
The inner disk rotates relative to the rotating shaft in a state where both axial side surfaces, which are toroidal curved surfaces having a circular arc cross section, are opposed to one axial side surface of the outer disks, around the middle portion of the rotating shaft. Is formed by combining a single element or a pair of elements that are freely supported.
Each of the supporting members is centered on a pivot that is twisted with respect to the rotating shaft, and a plurality of each of the supporting members is located between the axially opposite side surfaces of the inner disk and the axially one side surface of the outer disks. Is provided so that the swing displacement can be
Each of the power rollers is rotatably supported by each of the support members, and has a circumferential surface that is a partially spherical convex surface abutting on both axial sides of the inner disk and one axial side of the outer disks. Let
The pressing device is provided between the rotating shaft and the one outer disk, and presses the one outer disk toward the other outer disk.
The locking ring is locked in the locking groove, and one side surface in the axial direction thereof is brought into contact with the other side surface in the axial direction of the other outer disk facing in the axial direction. In a toroidal type continuously variable transmission that prevents displacement in a direction away from the one outer disk,
Torque transmission between the disks via the power rollers is achieved by separating one axial side surface of the locking ring and the edge of each spline groove constituting the spline hole with respect to the axial direction. Further, even when the other outer disk is elastically deformed, the axial side surface of the locking ring is prevented from coming into contact with the edge of each female spline groove constituting the spline hole. Toroidal-type continuously variable transmission.   In the state where the spline shaft portion is sandwiched from both sides in the axial direction on the outer peripheral surface of the tip end portion of the rotating shaft, the engaging groove has an outer diameter larger than the diameter of the circumscribed circle of the spline shaft portion, An outer peripheral side cylindrical surface portion that does not change the outer diameter of the twisted outer diameter, and an outer diameter of the other outer side disk adjacent to the spline hole on the other end in the axial direction adjacent to the spline hole. The inner peripheral surface side cylindrical surface portion that does not change is provided, and the inner peripheral surface side cylindrical surface portion and the outer peripheral surface side cylindrical surface portion are fitted by interference fitting with the spline shaft portion and the spline hole being spline engaged. The toroidal continuously variable transmission according to claim 1, which is combined.   An inward flange having an inner diameter smaller than the diameter of the inscribed circle of the spline hole is formed at an end portion on the other axial side surface of the inner peripheral surface of the other outer disk, and the inward flange is 3. The toroidal continuously variable transmission according to claim 1, wherein the toroidal continuously variable transmission is disposed between one axial side surface of the locking ring and an inner side surface of the locking groove.

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